WO2003081069A1 - Systeme de debrayage destine a une transmission a double embrayage d'un vehicule - Google Patents

Systeme de debrayage destine a une transmission a double embrayage d'un vehicule Download PDF

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Publication number
WO2003081069A1
WO2003081069A1 PCT/DE2003/000995 DE0300995W WO03081069A1 WO 2003081069 A1 WO2003081069 A1 WO 2003081069A1 DE 0300995 W DE0300995 W DE 0300995W WO 03081069 A1 WO03081069 A1 WO 03081069A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
rocker arm
release system
fork
rotary
Prior art date
Application number
PCT/DE2003/000995
Other languages
German (de)
English (en)
Inventor
Gerd Ahnert
Burkhard Pollak
Original Assignee
Luk Lamellen Und Kupplungsbau Beteiligungs Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Luk Lamellen Und Kupplungsbau Beteiligungs Kg filed Critical Luk Lamellen Und Kupplungsbau Beteiligungs Kg
Priority to AU2003222726A priority Critical patent/AU2003222726A1/en
Priority to DE10391761T priority patent/DE10391761D2/de
Priority to BR0303660-0A priority patent/BR0303660A/pt
Publication of WO2003081069A1 publication Critical patent/WO2003081069A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • F16D25/083—Actuators therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0684—Mechanically actuated clutches with two clutch plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
    • F16D2023/141—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings characterised by using a fork; Details of forks
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19228—Multiple concentric clutch shafts

Definitions

  • the invention relates to a clutch release system for a dual clutch transmission of a motor vehicle with a first clutch actuator, which acts to actuate a first clutch on a first release bearing, and with a second clutch actuator, which acts to actuate a second clutch on a second release bearing.
  • a dual clutch transmission has two input shafts, which must be connected to the engine independently of each other by means of a clutch.
  • dry clutches are used for a double clutch, although wet clutches can also be used.
  • the double clutch, the flywheel, the vibration dampers as well as the clutch release systems and clutch actuators must be matched to one another in such a way that the limited installation space is optimally used. All components should find their place in the clutch bell or on the gearbox.
  • the invention has for its object to propose a clutch release system for a dual clutch transmission, which ensures reliable operation of both clutches even in extremely cramped conditions.
  • this object is achieved according to the invention in that a first mechanical transmission link is arranged between the first clutch actuator and the first release bearing, and that a second mechanical transmission path is arranged between the second clutch actuator and the second release bearing.
  • the first mechanical transmission link comprises a first rocker arm, the end of which faces the first release bearing is designed as a release fork.
  • the movement of the first clutch actuator can be transmitted directly to the first release bearing via the first rocker arm and its release fork, the translation of the first rocker arm being able to be matched to the desired reduction in force.
  • the first mechanical transmission link can comprise a first pivot lever, the area of which facing the first release bearing is designed as a release element.
  • the first mechanical transmission path can comprise a first sliding fork arranged on a guide part.
  • the advantageous mounting of the first sliding fork by means of a sliding joint corresponds to the switching operations.
  • This variant also opens up other possibilities for clutch actuation.
  • the first mechanical transmission link can comprise a rotatably mounted first rotary fork.
  • the second mechanical transmission link can also comprise a second rocker arm, the end of which faces the second release bearing is designed as a release fork. This also results in the advantages already discussed in connection with the first rocker arm for the second mechanical transmission link.
  • a further embodiment of the invention provides that the second mechanical transmission link comprises a second pivot lever, the area facing the second release bearing is designed as a release element. This enables the same advantages to be achieved as with the first swivel lever.
  • the second mechanical transmission link can comprise a second sliding fork arranged on a sliding part.
  • this variant also opens up other possibilities for clutch actuation.
  • the second mechanical transmission link can also comprise a rotatably mounted second rotary fork.
  • a rotatably mounted second rotary fork there are other possibilities for arranging the corresponding release system.
  • first rocker arm and the second rocker arm are positioned at an oblique angle to one another. Different angular positions can be realized between the two rocker arms, but due to the oblique-angled positioning, a certain height offset of the rocker arms is required.
  • the advantage lies in the freely selectable angle size and in the possibility of designing the first rocker arm and the second rocker arm of identical construction.
  • rocker arm and the second rocker arm are positioned opposite one another in the extended position. This enables a considerable reduction in the axial overall length. The prerequisite for this reduction in the axial length is that the release fork of the first rocker arm and the release fork of the second rocker arm have different widths.
  • the release fork can thus grip around the other release fork so that both rocker arms can be positioned at the same axial height.
  • the bearing of the axis of the first rocker arm and the bearing of the axis of the second rocker arm are then preferably also positioned at the same axial height. So that can
  • Coupling actuators are connected to the rocker arms at the same axial height.
  • the use of the same parts is made possible for the two bearings.
  • first rocker arm and the second rocker arm are arranged overlapping one another on a common axis.
  • the first and the second rocker arms then preferably also have a common bearing.
  • Another advantage of this embodiment is that the entire assembly of the clutch release system can be carried out in one step and from one side. Thus, only one opening for the rocker arm system is required in the side wall of the clutch bell, which has a favorable effect on the mechanical strength of the clutch bell.
  • the two clutch actuators can be arranged on one side of the clutch bell or the transmission housing. Overall, the arrangement options for the clutch actuators in the installation space improve.
  • the second rocker arm is designed to be divided in the longitudinal direction, the two halves being arranged on both sides of the first rocker arm on the common axis.
  • the second rocker arm has a U-shaped profile, between the two lateral legs of which the first rocker arm is arranged. In this variant, the second rocker arm is thus formed in one piece.
  • rocker arm and rocker arm it is provided that a first rocker arm and a second rocker arm are combined with one another, or that a first rocker arm and a second rocker arm are combined with one another.
  • Such a combination of rocker arm and swivel lever enables, for example, separate storage of the two levers.
  • first sliding fork and a second sliding fork is provided.
  • storage of the sliding forks by sliding joints is particularly advantageous, since it corresponds to the switching operations.
  • This variant also opens up other possibilities for clutch actuation.
  • the combination of a first rotary fork and a second rotary fork is provided.
  • first rotary fork has a first rotary arm and that the second rotary fork has a second forked rotary arm, the first clutch actuator acting on the first rotary arm and the second clutch actuator acting on the second rotary arm being arranged coaxially are.
  • the two rotary arms thus enable the advantageous coaxial attachment of both clutch actuators.
  • first rotary fork is driven in rotation via a first pin
  • second rotary fork is driven in rotation via a second pin
  • the first pin is then preferably connected to the rotary shaft of a first clutch actuator via a first plug-in coupling
  • the second pin is connected to the rotary shaft of a second clutch actuator via a second plug-in coupling.
  • the rotary bearings of the first rotary fork and the rotary bearings of the second rotary fork are arranged together on the base plate of the guide tube of the release bearing.
  • the rotary forks with their pivot bearings are thus connected to the guide tube to form an assembly unit.
  • This assembly can then be mounted separately in the clutch bell or it can be fixed to the clutch unit in a cover-tight manner.
  • the clutch actuators With a combination of two rocker arms, which are arranged overlapping each other on a common axis, there are various possibilities for the arrangement of the clutch actuators.
  • a particularly advantageous arrangement is that the first clutch actuator and the second clutch actuator are arranged coaxially.
  • the actuator of the second clutch actuator can be passed through a hollow shaft of the first clutch actuator. Due to the coaxial arrangement, both clutch actuators can also be combined. In addition to a common assembly, this also makes it possible, for example, to implement a common housing with only one electrical plug connection.
  • Another advantageous arrangement variant provides that the first clutch actuator and the second clutch actuator are arranged coaxially opposite one another.
  • a rocker arm is designed as an angle lever and that the first clutch actuator and the second clutch actuator are positioned in an angular position relative to one another.
  • the formation of a rocker arm as an angle lever thus enables space-saving arrangement variants of the two clutch actuators.
  • FIG. 7 and 8 show a second embodiment of a clutch release system with two rocker arms in a partially sectioned top view and in a side view
  • Figure 9 shows a third embodiment of a clutch release system with two
  • FIG. 10 shows a side view of the release bearings arranged on a guide tube in the third embodiment according to FIG. 9,
  • FIG. 11 shows a partially sectioned top view of the third embodiment according to FIG. 9,
  • FIG. 12 shows a side view of the two rocker arms in an arrangement corresponding to FIG. 9,
  • FIG. 14 shows a section corresponding to FIG. 13 with a one-piece design of both rocker arms
  • FIGS. 15 and 16 show an embodiment of a clutch release system with a combination of rocker arm and pivot lever in the partially sectioned top view and in the side view
  • FIGS. 17 and 18 show an embodiment of a clutch release system with two sliding forks in cross section or in a partially sectioned top view
  • 19 and 20 show a first embodiment of a clutch release system with two rotary forks in the partially sectioned top view and in the side view
  • FIGS. 21 and 22 show a second embodiment of a clutch release system with two rotary forks in the partially sectioned top view and in the side view
  • FIG. 23 shows a first possibility of arranging the two clutch actuators in a clutch release system with two rocker arms
  • FIG. 24 shows a second possibility of arranging the two clutch actuators in a clutch release system with two rocker arms
  • Figure 25 shows a third possibility of arranging the two clutch actuators in a clutch release system with two rocker arms.
  • FIG. 1 and 2 show the principle of operation of a rocker arm designated 11 in a clutch release system.
  • This rocker arm 11 is pivotally mounted on an axle 110, the two ends of the axle 110 being each arranged in a bearing 111.
  • the rocker arm 11 is actuated by a clutch actuator, which is indicated in FIG. 2 only by a double arrow 112.
  • the end of the rocker arm 11 opposite the clutch actuator 112 is designed as a release fork 113.
  • the rocker arm 11 acts via its release fork 113 on a release bearing 116 which is fastened on a guide sleeve 114.
  • the guide sleeve 114 is in turn arranged on a guide tube 115.
  • the release bearing 116 can thus be displaced in the axial direction, as is indicated in FIG. 2 by the double arrow 117.
  • Figures 1 and 2 only show the principle of action of a rocker arm.
  • a second mechanical transmission element for example a second rocker arm, would be required in addition to the rocker arm.
  • FIG. 3 and 4 show the principle of action of a pivot lever designated 31 in a clutch release system.
  • This pivot lever 31 is pivotally mounted on an axis 310, the two ends of the axis 310 being arranged in a bearing 311.
  • the pivot lever 31 is actuated by a clutch actuator, which is indicated in FIG. 4 only by a double arrow 312.
  • the central region of the pivot lever 31 is designed as a disengagement element 313.
  • the release member 313 is formed by an approximately rectangular recess in the pivot lever 31, this shape can also be viewed as a closed release fork.
  • the pivot lever 31 acts via its disengaging member 313 on a disengaging bearing 316 which is fastened on a guide sleeve 314.
  • the guide sleeve 314 is in turn arranged on a guide tube 315.
  • Figures 3 and 4 only show the principle of action of a pivot lever.
  • a second mechanical transmission element for example a rocker arm or a second rocker arm, would be required in addition to the rocker arm.
  • FIGS. 5 and 6 show a first embodiment of a clutch release system with a first rocker arm 51 and a second rocker arm 55, these two rocker arms being positioned at an oblique angle to one another.
  • the first rocker arm 51 is pivotally mounted on an axis 510, the two ends of the axis 510 being arranged in a bearing 511, respectively.
  • the actuation of the The first rocker arm 51 is carried out by a first clutch actuator, which is indicated in FIG. 6 only by a double arrow 512.
  • the end of the first rocker arm 51 opposite the first clutch actuator 512 is designed as a release fork 513.
  • the second rocker arm 55 is pivotally mounted on an axis 550, the two ends of the axis 550 being arranged in a bearing 551, respectively.
  • the second rocker arm 55 is actuated by a second clutch actuator, which is indicated in FIG. 6 only by a double arrow 552.
  • the end of the second rocker arm 55 opposite the clutch actuator 552 is designed as a release fork 553.
  • the first rocker arm 51 acts via its release fork 513 on a first, inner release bearing 516, which is fastened on an inner guide sleeve 514.
  • the inner guide sleeve 514 is in turn arranged on a guide tube 515.
  • the second rocker arm 55 acts via its release fork 553 on a second, outer release bearing 556, which is fastened on an outer guide sleeve 554.
  • the outer guide sleeve 554 is also arranged on the guide tube 515.
  • FIGS. 7 and 8 show a second embodiment of a clutch release system with a first rocker arm 71 and a second rocker arm 75, these two rocker arms being positioned opposite one another in the extended position.
  • the first rocker arm 71 is pivotally mounted on an axis 710, the two ends of the axis 710 being each arranged in a bearing 711.
  • the first rocker arm 71 is actuated by a first clutch actuator, which is indicated in FIG. 8 only by a double arrow 712.
  • the end of the rocker arm 71 opposite the first clutch actuator 712 is designed as a release fork 713.
  • the second rocker arm 75 is pivotally mounted on an axis 750, the two ends of the axis 750 being each arranged in a bearing 751.
  • the second rocker arm 75 is actuated by a second clutch actuator, which is indicated in FIG. 8 only by a double arrow 752.
  • the end of the second rocker arm 75 opposite the clutch actuator 752 is designed as a release fork 753.
  • the first rocker arm 71 acts via its release fork 713 on a first, inner release bearing 716, which is fastened on an inner guide sleeve 714.
  • the inner guide sleeve 714 is in turn arranged on a guide tube 715.
  • the second rocker arm 75 acts via its release fork 753 on a second, outer release bearing 756, which is fastened on an outer guide sleeve 754.
  • the outer guide sleeve 754 is also arranged on the guide tube 715.
  • FIGS. 9 to 11 show a third embodiment of a clutch release system with a first rocker arm 91 and a second rocker arm 95, these two rocker arms being arranged overlapping one another and at least largely parallel to one another on a common axis 910.
  • the two ends of the common axis 910 are each arranged in a bearing 911.
  • the first rocker arm 91 is actuated by a first clutch actuator 912, the movement of which is indicated in FIG. 9 by a double arrow 9120.
  • the end of the first rocker arm 91 opposite the clutch actuator 912 is designed as a release fork 913.
  • the actuation of the split rocker arm 95 is carried out by a second clutch actuator 952, the movement of which is indicated in FIG. 9 by a double arrow 9520.
  • the end of the second rocker arm 95 opposite the second clutch actuator 952 is designed as a likewise split release fork 953.
  • FIG. 11 shows that the two halves of the second rocker arm 95 and its release fork 953 are arranged on both sides of the first rocker arm 91 on the common axis 910.
  • FIG. 11 also shows that the first clutch actuator 912 and the second clutch actuator 952 are arranged coaxially.
  • the first rocker arm 91 acts via its release fork 913 on a first, inner release bearing 916, which is fastened on an inner guide sleeve 914.
  • the inner guide sleeve 914 is in turn arranged on a guide tube 915.
  • the second split rocker arm 95 acts via its split release fork 953 on a second, outer release bearing 956, which is on an outer guide sleeve 954 is attached.
  • the outer guide sleeve 954 is in turn arranged on the inner guide sleeve 914 via an intermediate sleeve, which is not specified in any more detail.
  • the second outer release bearing 956 can thus be displaced in the axial direction, as is indicated in FIGS. 9 and 10 by a double arrow 957.
  • FIG. 12 shows a side view of two rocker arms in an arrangement corresponding to FIG. 9.
  • the first rocker arm 121 and the second rocker arm 125 are pivotally supported, overlapping one another and at least largely parallel to one another, on a common axis 1210, the two ends of the common axis 1210 each being arranged in a bearing 1211.
  • FIG. 13 shows in a section along the line Xlll-Xlll in FIG. 12 that the second rocker arm 125 is of split design, the two halves of the second rocker arm 125 being arranged on both sides of the first rocker arm 121 on the common axis 1210.
  • FIG. 14 shows a section comparable to FIG. 13, the first rocker arm being denoted by 141, the second rocker arm by 145, the common axis by 1410 and the bearing by 1411.
  • the second rocker arm 145 which is formed in one piece here, has a U-shaped profile, between the two side legs of which the first rocker arm 141 is arranged.
  • FIGS. 15 and 16 show an embodiment with a combination of a first rocker arm 151 and a second swivel lever 155, these two levers being positioned in an extended position with respect to one another.
  • the first rocker arm 151 is pivotally mounted on an axis 1510, the two ends of the axis 1510 each being arranged in a bearing 1511.
  • the first rocker arm 151 is actuated by a first clutch actuator, which is indicated in FIG. 16 only by a double arrow 1512.
  • the end of the first rocker arm 151 opposite the first clutch actuator 1512 is designed as a release fork 1513.
  • the second pivoting lever 155 is pivotably mounted on an axis 1550, the two ends of the axis 1550 each being arranged in a bearing 1551.
  • the second pivot lever 155 is actuated by a second clutch actuator, which is indicated in FIG. 16 only by a double arrow 1552.
  • the central region of the second pivot lever 155 is designed as a disengagement element.
  • this release member has the shape of a fork 1553, the two legs of which extend to the second clutch actuator 1552 and accommodate the entire rocker arm 151 between them.
  • the first rocker arm 151 acts via its release fork 1513 on a first inner release bearing 1516, which is fastened on an inner guide sleeve 1514.
  • the inner guide sleeve 1514 is in turn arranged on a guide tube 1515.
  • the second pivoting lever 155 acts via its fork 1553 on a second, outer release bearing 1556, which is fastened on an outer guide sleeve 1554.
  • the outer guide sleeve 1454 is also arranged on the guide tube 1515.
  • FIGS. 15 and 16 enables the two clutch actuators 1512 and 1552 to be arranged coaxially.
  • FIGS. 17 and 18 show an embodiment of a clutch release system with a first sliding fork 171 and a second sliding fork 175.
  • the first sliding fork 171 is arranged on a guide part 1710 so as to be displaceable in the axial direction.
  • the first sliding fork 171 is actuated by a first clutch actuator, which is indicated in FIG. 18 only by a double arrow 1712.
  • the second sliding fork 175 is arranged on a guide part 1750 so as to be displaceable in the axial direction.
  • the second sliding fork 175 is actuated by a second clutch actuator, which is indicated in FIG. 18 only by a double arrow 1752.
  • a first, inner disengagement position 1716 is displaced in the axial direction via the first sliding fork 171, as is indicated in FIG. 18 by a double arrow 1717.
  • a second, outer release bearing 1756 is displaced in the axial direction via the second sliding fork 175, as is indicated in FIG. 18 by a double arrow 1757.
  • the guide tube of the two release bearings 1716 and 1756 is designated 1715 in FIG.
  • FIGS. 19 and 20 show a first embodiment of a clutch release system with a first rotary fork 191 and a second rotary fork 195.
  • the first rotary fork 191 is arranged on both sides in rotary bearings 1911, their actuation being carried out by a first clutch actuator 1912 via a rotary arm 1910.
  • the resulting rotary movement of the first rotary fork 191 is indicated in FIG. 20 by a double arrow 19120.
  • the second rotary fork 195 is arranged on both sides in rotary bearings 1951, their actuation being carried out by a second clutch actuator 1952 via a forked rotary arm 1950.
  • the resulting rotary movement of the second rotary fork is indicated in Figure 20 by a double arrow 19520.
  • the two clutch actuators 1912 and 1950 are arranged coaxially.
  • a first inner release bearing 1916 is displaced in the axial direction via the first rotary fork 191, as is indicated in FIG. 20 by a double arrow 1917.
  • a second, outer release bearing 1956 is displaced in the axial direction via the second rotary fork 195, as is indicated in FIG. 20 by a double arrow 1957.
  • the guide tube of the two release bearings 1916 and 1956 is designated 1915 in FIG.
  • FIGS. 21 and 22 show a second embodiment of a
  • Clutch release system with a first rotary fork 211 and a second rotary fork
  • the first rotary fork 211 is arranged on both sides in pivot bearings 2111, their
  • Rotary shaft 21121 is carried out by a first clutch actuator 2112.
  • 215 is arranged on both sides in rotary bearings 2151, wherein they are actuated via a second pin 2150, a second plug-in coupling 21522 and a rotary shaft 21521 by a second clutch actuator 2152.
  • a first inner release bearing 2116 is displaced in the axial direction via the first rotary fork 211, as is indicated in FIG. 22 by a double arrow 2117.
  • a second, outer release bearing 2156 is displaced in the axial direction via the second rotary fork 215, as is indicated in FIG. 22 by a double arrow 2157.
  • the guide tube of the two release bearings 2116 and 2156 is designated by 2115 in FIG. 22.
  • the rotary bearings 2111 of the first rotary fork 211 and the rotary bearings 2151 of the second rotary fork 215 are jointly arranged on the base plate of the guide tube 2115 of the release bearings 2116 and 2156.
  • the rotary forks 211 and 215 with their pivot bearings 2111 and 2151 are thus connected to the guide tube to form an assembly unit.
  • This assembly can then be mounted separately in the clutch bell or it can be fixed to the clutch unit in a cover-tight manner.
  • the rotary shafts 21121 and 21521 with their plug-in couplings 21122 and 21522 are plugged onto the associated pins 2110 and 2150 of the rotary forks 211 and 215.
  • the mounting direction for the attachment of the first clutch actuator 2112 is shown in FIG. 22 by an arrow 21123.
  • FIGS. 23, 24 and 25 each show rocker arm arrangements of clutch release systems, on which three different possibilities for the attachment and arrangement of the two clutch actuators are shown by way of example.
  • FIG. 23 shows a first rocker arm 231 and a second rocker arm 235, these two rocker arms being arranged overlapping one another and at least largely aligned parallel to one another on a common axis 2310. The two ends of the common axis 2310 are each arranged in a bearing 2311.
  • the first rocker arm 231 is actuated by a first clutch actuator 2312 via an actuating element 23121 articulated on the lever end, the resulting movement being indicated by a double arrow 23120.
  • the first clutch actuator 2312 is, for example, an electrically driven actuator. Regardless of the type and design of the actuator, it is important in the exemplary embodiment shown that the first clutch actuator 2312 is equipped with a hollow shaft 23121.
  • the second rocker arm 235 is actuated by a second clutch actuator 2352 via an actuator 23521 articulated on the lever end, which is guided through the hollow shaft 23121 of the first clutch actuator 2312. This results in a coaxial arrangement of the two clutch actuators 2312 and 2352.
  • the two clutch actuators can also be combined. Thus e.g. a common housing with only one electrical connector or a common month can be realized.
  • FIG. 24 shows a first rocker arm 241 and a second rocker arm 245, these two rocker arms being arranged overlapping one another and at least largely aligned parallel to one another on a common axis 2410.
  • the two ends of the common axis 2410 are each arranged in a bearing 2411.
  • the first rocker arm 241 is actuated by a first clutch actuator 2412 via an actuating member 24121 articulated on the lever end, the resulting movement being indicated by a double arrow 24120.
  • the second rocker arm 245 is actuated by a second clutch actuator 2452 via an actuating member 24521 articulated at the end of the lever, the resulting movement being indicated by a double arrow 24520. It can be seen that the first clutch actuator 2412 and the second clutch actuator 2452 are arranged coaxially opposite one another with respect to the lever system.
  • FIG. 25 shows a first rocker arm 251 and a second rocker arm 255 designed as an angle lever, which are arranged on a common axis 2510.
  • the two ends of the common axis 2510 are each arranged in a bearing 2511.
  • the first rocker arm 251 is actuated by a first clutch actuator 2512 via an actuating member 25121 articulated on the lever end, the resulting movement being indicated by a double arrow 25120.
  • the second rocker arm 255 is actuated by a second clutch actuator 2552 via an actuating member 25521 articulated on the lever end, the resulting movement being indicated by a double arrow 25520.
  • first clutch actuator 2512 and the second clutch actuator 2552 are positioned in an angular position relative to one another, this space-saving arrangement being made possible by the formation of a rocker arm as an angle lever.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Structure Of Transmissions (AREA)
  • Retarders (AREA)
  • Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)
  • Control Of Transmission Device (AREA)

Abstract

L'invention concerne un système de débrayage destiné à une transmission à double embrayage d'un véhicule. Selon l'invention, un premier actionneur d'embrayage destiné à l'actionnement d'un premier embrayage agit sur un premier palier de débrayage par l'intermédiaire d'une première voie de transmission mécanique, et un deuxième actionneur d'embrayage agit sur un deuxième palier de débrayage par l'intermédiaire d'une deuxième voie de transmission mécanique. Les deux voies de transmission mécaniques peuvent de préférence faire intervenir des culbuteurs (11), des leviers pivotants (311), des fourches de poussée (171) ou des fourches rotatives (191), ainsi que des combinaisons de différents éléments telles que par ex. une combinaison de culbuteurs et de leviers pivotants.
PCT/DE2003/000995 2002-03-27 2003-03-26 Systeme de debrayage destine a une transmission a double embrayage d'un vehicule WO2003081069A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AU2003222726A AU2003222726A1 (en) 2002-03-27 2003-03-26 Clutch disengaging system for a twin clutch transmission of a motor vehicle
DE10391761T DE10391761D2 (de) 2002-03-27 2003-03-26 Kupplungsausrücksystem für ein Doppelkupplungsgetriebe eines Kraftfahrzeuges
BR0303660-0A BR0303660A (pt) 2002-03-27 2003-03-26 Sistema de desengate de embreagem para uma caixa de câmbio de embreagem dupla de um veìculo

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10213618 2002-03-27
DE10213618.1 2002-03-27
DE10236290.4 2002-08-08
DE10236290 2002-08-08

Publications (1)

Publication Number Publication Date
WO2003081069A1 true WO2003081069A1 (fr) 2003-10-02

Family

ID=28042863

Family Applications (3)

Application Number Title Priority Date Filing Date
PCT/DE2003/000994 WO2003081067A1 (fr) 2002-03-27 2003-03-26 Systeme a double embrayage destine a une transmission, notamment a une transmission a double embrayage
PCT/DE2003/000995 WO2003081069A1 (fr) 2002-03-27 2003-03-26 Systeme de debrayage destine a une transmission a double embrayage d'un vehicule
PCT/DE2003/000993 WO2003081066A1 (fr) 2002-03-27 2003-03-26 Unite de debrayage destinee aux embrayages d'une transmission a double embrayage d'un vehicule

Family Applications Before (1)

Application Number Title Priority Date Filing Date
PCT/DE2003/000994 WO2003081067A1 (fr) 2002-03-27 2003-03-26 Systeme a double embrayage destine a une transmission, notamment a une transmission a double embrayage

Family Applications After (1)

Application Number Title Priority Date Filing Date
PCT/DE2003/000993 WO2003081066A1 (fr) 2002-03-27 2003-03-26 Unite de debrayage destinee aux embrayages d'une transmission a double embrayage d'un vehicule

Country Status (9)

Country Link
US (2) US20050161302A1 (fr)
EP (1) EP1490603B1 (fr)
AT (1) ATE329171T1 (fr)
AU (3) AU2003223895A1 (fr)
BR (2) BR0303657A (fr)
DE (8) DE10391761D2 (fr)
FR (3) FR2837887B1 (fr)
IT (3) ITMI20030611A1 (fr)
WO (3) WO2003081067A1 (fr)

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EP1508715A3 (fr) * 2003-08-19 2005-06-15 Zf Friedrichshafen Ag Dispositif d'actionnement d'un embrayage double
DE102009039991A1 (de) 2008-09-15 2010-04-15 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Doppelkupplungsanordnung
DE202010012105U1 (de) 2010-09-02 2010-11-11 Klann-Spezial-Werkzeugbau-Gmbh Vorrichtung zur Einstellung einer Betätigungseinrichtung einer Doppelkupplung
CN101389879B (zh) * 2006-02-22 2011-01-12 罗伯特.博世有限公司 用于双离合器变速器的双离合器
KR101220370B1 (ko) * 2010-10-15 2013-01-09 현대자동차주식회사 차량의 더블 클러치용 클러치 포크 어셈블리
WO2013143394A1 (fr) 2012-03-31 2013-10-03 Shenzhen Byd Auto R&D Company Limited Mécanisme d'actionnement, ensemble d'embrayage à double action et véhicule
US8651255B2 (en) 2010-11-23 2014-02-18 Hyundai Motor Company Clutch actuating apparatus for double clutch transmission

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DE102004016177A1 (de) * 2004-03-30 2005-10-20 Volkswagen Ag Betätigungsvorrichtung zur Realisierung einer Kupplungsbetätigungsbewegung von mindestens einer Kupplungssteuereinrichtung eines Getriebes eines Kraftfahrzeuges
EP1596084A1 (fr) * 2004-05-13 2005-11-16 ZF Friedrichshafen AG Butée de débrayage d'un embrayage à friction d'un véhicule à moteur
DE502005002618D1 (de) * 2004-07-08 2008-03-13 Luk Lamellen & Kupplungsbau Vorrichtung zum Verbinden zweier Betätigungselemente mit zwei parallel zueinander bewegbaren Bauteilen, insbesondere Ein-/Ausrückbauteilen einer Doppelkupplung
FR2880932B1 (fr) * 2005-01-18 2008-07-25 Valeo Embrayages Element de transmission a palier de centrage et de reprise d'effort
EP1785640B1 (fr) * 2005-11-11 2010-01-06 LuK Lamellen und Kupplungsbau Beteiligungs KG Dispositif d'actionnement pour une boîte de vitesses à double embrayage.
ATE515646T1 (de) * 2006-09-16 2011-07-15 Schaeffler Technologies Gmbh Anordnung zur betätigung einer kupplung
DE102006045163A1 (de) 2006-09-25 2008-04-03 Robert Bosch Gmbh Doppelkupplung für ein Doppelkupplungsgetriebe
DE102008012903A1 (de) 2008-03-06 2009-09-17 Robert Bosch Gmbh Antrieb für ein Hybridfahrzeug sowie Kupplung mit einer Ausrückvorrichtung
DE102008012894A1 (de) * 2008-03-06 2009-09-10 Zf Friedrichshafen Ag Betätigungseinrichtung für eine Reibungskupplungseinrichtung und von diesen gebildete Drehmomentübertragungseinrichtung
AU2009279386A1 (en) 2008-08-08 2010-02-11 Osprey Medical Inc. Reverse catheter
FR2941755B1 (fr) * 2009-01-30 2011-04-08 Valeo Embrayages Mecanisme a double embrayage comportant un dispositif de commande a double fourchette
FR2951791B1 (fr) * 2009-10-27 2012-04-27 Valeo Embrayages Dispositif de commande pour un mecanisme d'embrayage presentant un encombrement longitudinal reduit.
CN103314232B (zh) * 2010-03-25 2016-01-20 舍弗勒技术股份两合公司 双离合器
DE102012208655A1 (de) * 2011-06-14 2012-12-20 Schaeffler Technologies AG & Co. KG Aktorsystem für Doppelkupplung
DE102013223601A1 (de) 2013-11-19 2015-05-21 Schaeffler Technologies AG & Co. KG Antriebsstrang
DE102014210773A1 (de) * 2014-01-09 2015-07-09 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Kupplungsbaugruppe für die Kupplungsbetätigung in einem Fahrzeuggetriebe
DE102014218781B3 (de) * 2014-09-18 2016-03-24 Schaeffler Technologies AG & Co. KG Betätigungssystem mit Ausgleich einer achsialen Verschiebung in der Verbindungsstrecke zwischen Aktorik und Betätigungslager
DE102014224330A1 (de) 2014-11-28 2016-06-02 Schaeffler Technologies AG & Co. KG Mechanischer Zentralausrücker mit in Vertiefung eingreifendem Wälzkörper
DE102017211809A1 (de) * 2017-07-11 2019-01-17 Zf Friedrichshafen Ag Antriebseinheit für ein Kraftfahrzeug mit einer elektrischen Maschine und einer Kupplung

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GB1037523A (fr) *
US2573010A (en) * 1949-07-08 1951-10-30 Wayne L Groninger Farm tractor double clutch and drive
DE3138208A1 (de) * 1981-09-25 1983-02-17 Daimler-Benz Ag, 7000 Stuttgart "kraftuebertragungseinrichtung fuer kraftfahrzeuge, insbesondere schlepper
EP0628741A1 (fr) * 1993-06-07 1994-12-14 NEW HOLLAND ITALIA S.p.A. Ensemble d'accouplement de véhicule, notamment pour tracteurs
US5996754A (en) * 1998-09-15 1999-12-07 Chrysler Corporation Electro-mechanical clutch actuator

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1508715A3 (fr) * 2003-08-19 2005-06-15 Zf Friedrichshafen Ag Dispositif d'actionnement d'un embrayage double
CN101389879B (zh) * 2006-02-22 2011-01-12 罗伯特.博世有限公司 用于双离合器变速器的双离合器
DE102009039991A1 (de) 2008-09-15 2010-04-15 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Doppelkupplungsanordnung
DE202010012105U1 (de) 2010-09-02 2010-11-11 Klann-Spezial-Werkzeugbau-Gmbh Vorrichtung zur Einstellung einer Betätigungseinrichtung einer Doppelkupplung
DE102011110297A1 (de) 2010-09-02 2012-03-08 Klann-Spezial-Werkzeugbau-Gmbh Vorrichtung zur Einstellung einer Betätigungseinrich-tung einer Doppelkupplung
DE102011110297B4 (de) * 2010-09-02 2012-10-18 Klann-Spezial-Werkzeugbau-Gmbh Vorrichtung zur Einstellung einer Betätigungseinrich-tung einer Doppelkupplung
KR101220370B1 (ko) * 2010-10-15 2013-01-09 현대자동차주식회사 차량의 더블 클러치용 클러치 포크 어셈블리
US8651255B2 (en) 2010-11-23 2014-02-18 Hyundai Motor Company Clutch actuating apparatus for double clutch transmission
WO2013143394A1 (fr) 2012-03-31 2013-10-03 Shenzhen Byd Auto R&D Company Limited Mécanisme d'actionnement, ensemble d'embrayage à double action et véhicule
EP2831439B1 (fr) * 2012-03-31 2020-04-29 Shenzhen BYD Auto R&D Company Limited Mécanisme d'actionnement, ensemble d'embrayage à double action et véhicule

Also Published As

Publication number Publication date
ITMI20030610A1 (it) 2003-09-28
DE10391758D2 (de) 2005-02-10
AU2003222727A1 (en) 2003-10-08
EP1490603B1 (fr) 2006-06-07
FR2838169B1 (fr) 2005-05-06
BR0303660A (pt) 2004-07-13
ATE329171T1 (de) 2006-06-15
FR2837887A1 (fr) 2003-10-03
DE10391758B4 (de) 2016-12-08
US20050161302A1 (en) 2005-07-28
DE10313382A1 (de) 2003-10-09
ITMI20030612A1 (it) 2003-09-28
DE10391761D2 (de) 2004-05-27
FR2838797B1 (fr) 2005-06-17
US7905338B2 (en) 2011-03-15
US20100006386A1 (en) 2010-01-14
BR0303657A (pt) 2004-07-13
DE50303693D1 (de) 2006-07-20
FR2837887B1 (fr) 2005-05-06
EP1490603A1 (fr) 2004-12-29
DE10391759D2 (de) 2005-01-27
AU2003222726A1 (en) 2003-10-08
AU2003223895A1 (en) 2003-10-08
DE10313383A1 (de) 2003-12-24
FR2838797A1 (fr) 2003-10-24
WO2003081067A1 (fr) 2003-10-02
ITMI20030611A1 (it) 2003-09-28
DE10313380A1 (de) 2003-10-09
DE10313435A1 (de) 2003-10-09
FR2838169A1 (fr) 2003-10-10
WO2003081066A1 (fr) 2003-10-02

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